EP2526286A1

EP2526286A1 - Device for controlling the movement of a ring gate of a hydraulic machine and hydraulic machine comprising such a device

Info

Publication number: EP2526286A1
Application number: EP11705916A
Authority: EP
Inventors: Robert Pavillet; Armin Steinhilber
Original assignee: Alstom Hydro France SAS
Current assignee: GE Renewable Technologies Wind BV
Priority date: 2010-01-21
Filing date: 2011-01-20
Publication date: 2012-11-28
Anticipated expiration: 2031-01-20
Also published as: FR2955369A1; RU2012135685A; CN102725514B; BR112012018194A2; WO2011089361A1; US20130098237A1; CA2787361A1; ES2559206T3; FR2955369B1; MX2012008487A; PT2526286E; US9494173B2; CN102725514A; CA2787361C; RU2546346C2; EP2526286B1; BR112012018194B1; CO6612236A2; PE20141623A1

Abstract

The invention relates to a device (1), which controls the movement of a ring gate (2) of a hydraulic machine between an open position and a blockage position. The device (1) includes at least four cylinders (11, 12, 21, 22, 31, 32), the rods (11.3, 12.3) of which are suitable for being connected to the ring gate (2) at locations located on a perimeter (C2) of the ring gate (2). The device (1) also includes at least two hydraulic members (10.1, 20.1, 30.1) for synchronising pistons (11.4, 12.4), the hydraulic synchronisation members (10.1, 20.1, 30.1) being connected to the cylinders (11, 12, 21, 22, 31, 32) such as to form at least two groups (10, 20, 30). Each group (10, 20, 30) encompasses at least two cylinders (11-12, 21-22, 31-32) connected by at least one hydraulic synchronisation member (10.1, 20.1, 30.1), two cylinders (11, 21, 31, 12, 22, 32) belonging to two separate groups (10, 20, 30) not being connected by a hydraulic synchronisation member (10.1, 20.1, 30.1).

Description

DEVICE FOR CONTROLLING THE MOVEMENT OF A

HYDRAULIC MACHINE FITTING VALVE AND HYDRAULIC MACHINE COMPRISING SUCH A DEVICE

The present invention relates to a device for controlling the movement of a hydraulic machine sleeve valve. Furthermore, the present invention relates to a hydraulic machine comprising such a device. The present invention can be applied in particular to turbines, pumps or pump turbines.

A prior art hydraulic machine comprises a paddle wheel and a slider valve for controlling the water supply of the impeller. The slit valve is movable between an open position and a closed position of a water supply line of the impeller. The movement of the sheath valve between its open and closed positions is controlled by an electro-hydraulic control device.

A control device of the prior art comprises cylinders with double hydraulic action each comprising a rod and a piston which separates two chambers adapted to receive an actuating fluid of the jack. Such a control device also requires mechanical components to synchronize the movements of the piston cylinders. In particular, among the mechanical components associated with each jack, a reversible screw-nut couple transforms the translation of the piston and the rod in rotation of an external pinion to the jack. In addition, a transmission chain connects the gears with each other so as to synchronize their rotations and consequently to synchronize the translations of the pistons of the different cylinders.

However, this control device comprises, for each cylinder, several mechanical components that require delicate adjustments and tedious maintenance interventions.

The present invention aims to overcome these disadvantages by providing a reliable control device and simple to adjust. For this purpose, the present invention relates to a device for controlling the displacement of a hydraulic machine sleeve valve comprising a blade wheel, the sleeve valve defining a closed contour and being movable between an open position and a closed position of at least one water supply line of the impeller, the device comprising at least four double-acting hydraulic cylinders, each cylinder comprising:

- a rod,

- A piston,

- a first room and

- a second bedroom

the first chamber and the second chamber being adapted to receive an actuating fluid, the piston being connected to the stem so as to separate the first chamber from the second chamber, the first chamber being located on the side of the rod with respect to the piston and the second chamber being located on the opposite side to the rod relative to the piston, the rods being adapted to be connected to the sleeve valve at locations situated on a perimeter adapted to coincide with the contour of the slider valve,

The device further comprises at least two hydraulic synchronization units of the distances traveled by pistons in the main direction of movement of the sleeve valve, the hydraulic synchronizing members being connected to the cylinders so as to form at least two distinct groups of cylinders , each group including at least two jacks connected by at least one hydraulic synchronizing member, two jacks belonging to two distinct groups not being connected by a hydraulic synchronizing member.

A control device according to the invention thus makes it possible to synchronize the jacks effectively.

According to other advantageous but optional features of the invention, taken alone or in any technically permissible combination: the locations are distributed on the perimeter so that the stiffness of the slider valve contributes to synchronize the distances traveled by pistons belonging to distinct groups, according to the main direction of movement of the slider valve;

at least one hydraulic synchronization device comprises a conduit arranged to connect in series at least two cylinders belonging to the same group, namely a first cylinder and a second cylinder, said hydraulic synchronizing device being adapted for the fluid flow of actuating the first chamber of a first cylinder to the second chamber of a second cylinder, the second cylinder being consecutive to the first cylinder in their group, the surface area of the piston face delimiting the first chamber of the first cylinder being approximately equal on the surface of the piston face delimiting the second chamber of the second cylinder;

the number of jacks is between 5 and 30;

the groups include the same number of cylinders;

the device comprises at least three groups of jacks and each group includes two jacks;

two consecutive locations on said perimeter correspond to jacks belonging to two distinct groups;

the locations are uniformly distributed over said perimeter, said perimeter is in the form of a circle and the locations corresponding to the two cylinders of a group are diametrically opposed;

the first chamber and the second chamber of each jack are generally in the form of cylinders with circular bases;

for a first cylinder and a second cylinder belonging to the same group, the difference between the square of the internal diameter of the first cylinder and the square of the internal diameter of the second cylinder is equal to the square of the diameter of the rod of the first cylinder;

the device furthermore comprises a control unit and means for discrete supply and / or discrete discharge of operating fluid for each jack, each cylinder is equipped with at least one sensor adapted to emit signals representative of the position of the corresponding piston in the direction of actuation of the jack, the control unit being arranged to collect said signals and adapted to control the discrete supply means and / or discrete evacuation taking into account the positional deviations, in the main direction of movement of the sleeve valve, between jacks belonging to the same group; and

the device further comprises means for continuously feeding and / or continuously discharging actuating fluid from the jacks and the driving unit is adapted to control the continuous feed and / or continuous discharge means in taking into account positional deviations between cylinders belonging to distinct groups.

Moreover, the subject of the present invention is a hydraulic machine, of the turbine, pump or turbine-pump type, comprising a paddle wheel and a slider valve movable between an open position and a closed position of at least a water supply pipe of the impeller, the hydraulic machine being characterized in that it further comprises a device as previously exposed.

The present invention will be well understood and its advantages will also emerge in the light of the description which follows, given solely by way of nonlimiting example and with reference to the appended drawings, in which:

- Figure 1 is a schematic view of a device according to a first embodiment of the invention;

- Figure 2 is a section of a hydraulic machine according to the invention comprising the device of Figure 1;

FIG. 3 is an enlarged view of detail III in FIG. 1;

- Figure 4 is a section along the arrows IV-IV in Figure 3;

FIG. 5 is a schematic view partially in perspective of a part of the control device of FIG. 1; FIG. 6 is a schematic view of the sleeve valve, in a static phase, shown schematically in FIG. 1;

FIG. 7 is a view similar to FIG. 6 illustrating the slider valve of FIG. 6 in a dynamic phase; and - Figure 8 is a view similar to Figure 1 illustrating a control device according to a second embodiment of the invention.

FIG. 1 shows a device 1 for controlling the displacement of a sleeve valve 2. The sleeve valve 2 is shown schematically in phantom in FIG. 1 and shown in perspective in FIG. 6. The sleeve valve 2 generally defines a closed contour, as shown in Figure 6. In other words, the sleeve valve 2 has a generally annular shape. In the example of FIG. 6, the sheath valve 2 is in the form of a cylindrical ring with a circular base and a Y2-V2 axis visible in FIG. 2. The sheath valve 2 is shown diagrammatically in FIG. the way of a developed to facilitate the reading of Figure 1.

As shown in Figure 2, a hydraulic machine M according to the invention comprises a paddle wheel R, the sleeve valve 2 and the device 1. The sleeve valve 2 moves in a main direction Y, which is vertical and parallel to the axis Y2-Y'2 in the example of the figures. The sleeve valve 2 is movable between an open position and a closed position (FIG. 2) of a water supply line 5 for the impeller R. In the case of the hydraulic machine M, which can be turbine, pump or turbine-pump type, the pipe 5 is formed by a shell called "tarp". The slotted valve 2 is installed between the front-guiding lines 9 and the moving guides 6 which serve to direct the flow of water towards the paddle wheel R.

As shown in FIGS. 1 and 2, the device 1 comprises six cylinders 1 1, 12, 21, 22, 31 and 32 with double hydraulic action, each comprising:

a rod 1 1 .3, 12.3 or equivalent;

a piston 1 1 .4, 12.4 or equivalent;

a first chamber 1 1 .1, 1 2.1 or equivalent; and a second chamber 11.2, 12.2 or equivalent.

Insofar as the cylinders 11, 21 and 31, on the one hand, and the cylinders 12, 22 and 32, on the other hand, are similar or identical, only the cylinders 11 and 12 will be described in detail hereinafter. The description of the cylinders 11 and 12 given below in connection with the figures can be transposed to the cylinders 21, 22, 31 and 32.

As the cylinders 11 and 12 are cylinders with double hydraulic action, their first chambers 11.1 and 12.1 and their second chambers 11.2 and 12.2 are adapted to receive an actuating fluid, such as oil. Pistons 11.4 and 12.4 have generally planar faces. Each piston 11.4 or 12.4 is connected to the corresponding rod 11.3 or 12.3 so as to separate the respective first chamber 11.1 or 12.1 of the respective second chamber 11.2 or 12.2.

The first chamber 11.1 or 12.1 and the second chamber 11.2 or 12.2 of each cylinder 11 and 12 are generally in the form of cylinders with circular bases. Similarly, the rod 11.3 is cylindrical. Each first chamber 11.1 or 12.1 is located, relative to the piston 11.4 or 12.4, on the corresponding rod 11.3 or 12.3 side, while each second chamber 11.2 or 12.2 is located, relative to the piston 11.4 or 12.4, the opposite side to the corresponding rod 11.3 or 12.3. In other words, the rod 11.3 or 12.3 partially enters the respective first chamber 11.1 or 12.1, while the second chamber 11.2 or 12.2 contains only the actuating fluid.

The rods 11.3, 12.3 and equivalents are adapted to be connected to the slit valve 2 at locations P11, P12, P21, P22, P31 and P32 located on a perimeter C2 coinciding with the contour of the slider valve 2. In the In this application, the verb "bind" refers to a mechanical connection.

In this case, one end of each rod 11.3 or 12.3 is directly attached to the circular contour of the sleeve valve 2. As far as the perimeter C2 on which are located the locations P11, P12, P21, P22, P31 and P32 connection between rods 11.3, 12.3 and equivalents and sleeve valve 2 is adapted to coincide with the circular contour of the sleeve valve 2, this perimeter C2 is also circular. The device 1 comprises three ducts 10.1, 20.1 and 30.1 which are arranged to connect in series two respective cylinders January 1 and 12, 21 and 22 or 31 and 32. Thus, the conduit 10.1 connects in series the cylinders January 1 and 12. The conduit 20.1 connects the jacks 21 and 22 in series. The conduit 30.1 connects the jacks 31 and 32 in series.

In the present application, the verbs "connect", "connect", "connect" and "drive", as well as their derivatives means "put into hydraulic communication". The adjective "hydraulic" may refer to an actuating fluid of the cylinders, such as oil, or to water flowing in the hydraulic machine.

The conduit 10.1 forms a synchronizing hydraulic unit, since it makes it possible to synchronize the distances traveled by the pistons 1 1 .4 and 1 2.4 in the direction Y. The maximum distance that the piston 1 1 .4 can travel in the direction Y corresponds to to the total stroke of the piston 1 1 .4 in the cylinder 1 1. Like the duct 10.1, each duct 20.1 or 30.1 makes it possible to synchronize the distances traveled by the pistons of the cylinders 21 and 22, on the one hand, and 31 and 32, on the other hand, in the Y direction. In the example of the figures, the pistons 1 1 .4, 12.4 and equivalents move in parallel and in the same direction in the direction Y. The hydraulic synchronization members that the ducts constitute

10.1, 20.1 and 30.1 are connected to the cylinders January 1, 12, 21, 22, 31 and 32 so as to form three groups 10, 20 and 30 distinct. Each group 10, 20 or 30 includes in this case two jacks 1 1 and 1 2, 21 and 22 or 31 and 32. Thus, two jacks 1 1 and 1 2, 21 and 22 or 31 and 32 belonging to the same group 10, 20 or 30 are connected in series by a respective conduit 1 0.1, 20.1 or 30.1. But two jacks 1 1 -21, 12-22 belonging to two distinct groups 10, 20 are not connected by a conduit 10.1, 20.1 or 30.1. The mode of synchronization specific to the example of the figures will be described in detail below.

In the present application, the term "group" designates an assembly encompassing at least two jacks connected by at least one hydraulic synchronization member. Groups 10, 20 and 30 encompass the same number of cylinders, namely two each. The device 1 comprises three groups 10, 20 and 30 which each include two cylinders January 1 and 12, 21 and 22, 31 and 32.

Moreover, as shown in FIGS. 5, 6 and 7, the locations P1 1, P12, P21, P22, P31 and P32 corresponding to the jacks 1 1, 12, 21, 22, 31 and 32 are distributed over the perimeter C2 of FIG. so that the stiffness of the sheath valve 2 helps to synchronize the distances traveled in the Y direction of the pistons, for example 1 1 .4 and 21 .4, which belong to groups 10, 20 and 30 separate.

On the perimeter C2, two consecutive locations correspond to cylinders belonging to two groups 10, 20 and 30 distinct. Thus, the locations P1 1 and P21 correspond to the jacks 1 1 and 21 which belong respectively to the group 10 and the group 20. Such a sequence makes it possible to alternate the locations P1 1, P12, P21, P22, P31 and P32, which helps to synchronize the piston cylinders as described below. In the example of FIGS. 5 to 7, the locations P1 1, P12, P21, P22,

P31 and P32 are uniformly distributed over the perimeter C2. In other words, two consecutive locations P1 1 and P21 are separated by an angle of 60 ° in the center of circular perimeter C2. In addition, the locations corresponding to the two cylinders of each of the groups 10, 20 and 30 are diametrically opposed on the perimeter C2. For example, the locations P1 1 and P12 corresponding to the cylinders 1 1 and 1 2 of the group 10 are diametrically opposed. Such a distribution of locations corresponding to the cylinders allows efficient mechanical synchronization by the stiffness of the sleeve valve 2. In Figure 1, the two cylinders of each group 10, 20 or 30 are shown schematically at adjacent locations. However, the function of FIG. 1 is to schematize electrical and hydraulic circuits of the device 1, not to represent the actual locations of the jacks or the components of the device 1 with respect to the sheath valve 2. These actual locations are shown in the figures 2 and 5 to 7. For the clarity of Figure 5, only the cylinders January 1 and 12 are shown. FIG. 6 symbolizes the contour of the sheath valve 2 coinciding with the perimeter C2, when the jacks are in a static phase, that is to say when the sheath valve 2 is not moving because it is placed in the open position or in the closed position. Figure 7 symbolizes the perimeter C2 when the cylinders are in a dynamic phase, that is to say when the sleeve valve 2 is moving.

In dynamic phase, the upper contour of the sheath valve 2 coinciding with the perimeter C2 is deformed, the deformed being shown in Figure 7 by a perimeter C2.1. For the understanding of FIG. 7, the perimeter C2.1 illustrates a distortion of the perimeter C2 in an amplified manner. In fact, as a function of the forces applied to the sleeve valve 2 by the external elements, for example by the hydraulic forces and by the friction forces, the jacks are not perfectly synchronized, but on the contrary have gaps between groups 10, 20 and 30. Thus, in the direction of the rise of the sleeve valve 2, the cylinders 31 and 32 can be "in advance", while the jacks 21 and 22 can be "late" with respect to the cylinders 1 1 and 12.

Insofar as the locations P1 1, P12, P21, P22, P31 and P32 are distributed over the perimeter C2, the stiffness of the sheath valve 2 ensures mechanical synchronization of the distances traveled by pistons such as 1 1 .4 and 21 .4 belonging to groups 10, 20 and 30 distinct. The stiffness of the sheath valve 2 is determined by its dimensions and by the elasticity of the material constituting it.

The diameter of the perimeter C2 corresponding to the sheath valve 2 may for example be between 2 m and 15 m. The material constituting the sheath valve 2 may for example be a steel. The height H2 of the sheath valve 2, measured in the Y direction, can be between 0.25 m and 3 m. The thickness of the sleeve valve 2, measured in a radial direction orthogonal to the Y direction, may be between 30 mm and 300 mm. In other words, the stiffness of the sheath valve 2 tends to bring the perimeter C2.1 of the deformation in dynamic phase in the vicinity of the perimeter C2 coinciding with the contour of the sheath valve 2 in the static phase, in opposing the forces that caused the deformation of the sheath valve 2. The stiffness of the sheath valve 2 contributes to synchronize the cylinders of groups 1 0, 20 and 30 separate. In the example of FIG. 7, the stiffness of the sheath valve 2 "brakes" the forward cylinders 31 and 32 and "accelerates" the lagging cylinders 21 and 22 at the jacks 11 and 12.

The hydraulic synchronization between cylinders of the same group is described below in relation to FIGS. 1 to 4, in particular between the jacks 1 1 and 12. When the sleeve valve 2 moves in the direction Y and in the direction the descent, the actuating fluid flows from the first cylinder 1 1 to the second cylinder 12. The terms "first" and "second" are chosen arbitrarily to designate the two consecutive cylinders of the same group.

The duct 1 0.1, or hydraulic synchronizing member, is adapted for the flow of actuating fluid between the first chamber 1 1 .1 of the first cylinder 1 1 and the second chamber 12.2 of the second cylinder 1 2. The second cylinder 12 is consequent to the first cylinder 1 1 in the group 1 0. In other words, the conduit 10.1 connects a discharge port / supply of the first chamber 1 1 .1 of the first cylinder 1 1 to a supply / discharge port the second chamber 12.2 of the second cylinder 12.

In addition, as shown in FIGS. 3 and 4, the surface area S1 1 .41 of the face 1 1 .41 of the piston 1 1 .4 which delimits the first chamber 1 1 .1 of the first jack 1 1 is approximately equal to the surface S1 2.42 of the face 12.42 of the piston 12.4 delimiting the second chamber 1 2.2 of the second cylinder 1 2. The areas S1 1 .41 and S12.42 respectively correspond to the flow sections of the first chamber 1 1 .1 of the cylinder 1 1 and of the second chamber 12.2 of the cylinder 12.

In this application, the term "approximately" reflects the manufacturing tolerances of the component parts of the cylinders. The equality between the areas S1 1 .41 and S12.42 is obtained by dimensioning the jacks 1 1 and 12 according to the following relation: D 1 1 ² = D 12 ² + D 1 .3 ² (1) where: D1 1 is the internal diameter of the cylinder 1 1,

D1 2 is the internal diameter of the cylinder 12 and

D1 1 .3 is the diameter of the rod 1 1 .3.

The internal diameter D1 1 of the cylinder 1 1 is therefore greater than the internal diameter D12 of the cylinder 12.

More generally, for a first cylinder and a second cylinder belonging to the same group, in particular to a group comprising more than two cylinders, the difference between the square of the internal diameter of the first cylinder and the square of the internal diameter of the second cylinder is the same. square of the diameter of the rod of the first cylinder.

As shown in Figure 4, the face 1 1 .41 has the shape of a crown, while the face 12.42 has the shape of a solid disc. The area S1 1 .41 is worth:

S1 = 1 .41 TT (D1 1) ^2/4 -. Ττ. (D1 ^{1 .3) 2/4 (2} )

In addition, the area S12.42 is: S12.42 = TT (D12) ^2/4 (3).

The equality between the areas S1 1 .41 and S1 2.42 allows the pistons 1 1 .4 and 12.4 of the cylinders 1 1 and 12 to move the same distance when a volume of operating fluid is transferred from the cylinder 1 1 to the cylinder 12 through the conduit 10.1 which forms a hydraulic synchronizing member pistons 1 1 .4 and 12.4. Furthermore, the device 1 comprises a control unit 4, three proportional distributors 71, 72 and 73, as well as three distributors 74, 75 and 76. Each proportional distributor 71, 72 or 73 is connected to a respective group 10, 20 or 30. Each proportional distributor 71, 72 or 73 has four inputs and three positions. The control unit 4 and the proportional distributors 71, 72 and 73 make it possible to control the flows of operating fluid between a source 3 of hydraulic fluid, the jacks 1 1, 12, 21, 22, 31 and 32 and a collector or drain 8.

In operation, to move the sleeve valve 2 in the direction of descent, the control unit 4 controls the proportional distributors 71, 72 and 73 so that the actuating fluid flows from the source 3 to the second chambers 1 1 .2 and equivalents of the first cylinders 1 1, 21 and 31. At the same time, the actuation fluid present in the first chambers 1 1 .1 and equivalent of the "first" cylinders January 1, 21 and 31 flows in the ducts 10.1, 20.1 and 30.1 respectively to the second chambers 12.2 and equivalent of " second »cylinders 1 2, 22 and 32. The ducts 1 0.1, 20.1 and 30.1 thus fulfill their function of hydraulic synchronizing pistons 1 1 .4, 1 2.4 and equivalent. Each duct 10.1, 20.1 or 30.1 synchronizes two pistons 1 1 .4 and 1 2.4 of cylinders belonging to the same group 10, 20 or 30. To move the sleeve valve 2 in the upward direction, the control unit 4 pilot proportional distributors 71, 72 and 73 so that the actuating fluid flows in opposite directions relative to the descent of the sleeve valve 2 described above.

As shown in Figures 1 and 5, the device 1 further comprises distributors 74, 75 and 76 connected respectively to each conduit 10.1, 20.1 and 30.1 .. The distributors 74, 75 and 76 are connected to the source 3 and the drain 8. In each group 10, 20 or 30, the respective distributor 74, 75 or 76 performs the function of discrete supply means and / or discrete evacuation for each cylinder 1 1 and 12 and equivalent operation fluid. In the present application, the term "discrete" applies to the flow, supply or discharge, small volumes of actuating fluid, as opposed to "continuous" flows of large volume of actuating fluid. Feeding means "continuous" and / or "continuous" evacuation of operating fluid is implemented to move the sleeve valve in a large amplitude, typically to move from the open position to the position of shutter. A "discrete" supply means and / or "discrete" evacuation of actuating fluid is implemented to move the rods and pistons of some cylinders with a small amplitude, the sheath valve then moving a insignificant distance or zero.

Each cylinder 1 1, 12, 21, 22, 31 or 32 is equipped with a sensor 1 1 .5, 12.5 and equivalent adapted to emit signals representative of the position of respective pistons 1 1 .4, 12.4 and equivalent in the direction Y. As shown in Figure 1, the control unit 4 is electrically connected to each sensor 1 1 .5, 12.5 and equivalent, so as to collect these signals.

The control unit 4 is adapted to control each distributor 74, 75 or 76, taking into account the positional deviations, in the Y direction, between the pistons 1 1 .4 and 1 2.4 of jacks 1 1 and 12 belonging to a same group 10, 20 or 30. In other words, each distributor 74, 75 or 76 can accurately synchronize the pistons cylinders belonging to the same group.

The control unit 4 is adapted to control the proportional distributors 71, 72 and 73 fulfilling the functions of continuous supply means and / or continuous discharge of actuating fluid for the respective cylinders 1 1 -12, 21 - 22 or 31 -32, taking into account the differences in position between the pistons of cylinders belonging to distinct groups such as 1 0 and 20, such as the cylinders January 1 and 21. In other words, each proportional distributor 71, 72 or 73 makes it possible to precisely synchronize pistons of cylinders belonging to distinct groups.

The proportional distributors 71, 72 and 73 and the distributors 74, 75 and 76 make it possible to ensure very high precision in the hydraulic synchronization of the distances traveled by the pistons 1 1 .4, 12.4 and equivalent of the cylinders 1 1, 12, 21 , 22, 31 and 32, in addition to the hydraulic synchronization achieved by the ducts 10.1, 20.1 and 30.1 and the mechanical synchronization achieved by the stiffness of the sheath valve 2.

FIG. 8 illustrates a device 110 in accordance with a second embodiment of the invention. The description of the device 1 given above may be transposed to the device 1 01, with the exception of the significant differences mentioned below. An element of the device 101 identical or corresponding to an element of the device 1 has the same numerical reference increased by 100.

Thus, a slit valve 102, a source 103 of hydraulic fluid, a control unit 104, three groups 110, 120 and 130 with cylinders 11, 12, 21, 122, 131 and 132 are defined. each cylinder 1 1 1, 1 12 or equivalent comprising a piston 1 1 1 .4, 1 12.4 or equivalent, a first chamber 1 1 1 .1, 1 12.1 or equivalent and a second chamber 1 1 1 .2, 1 12.2 or equivalent. The device 101 differs from the device 1, since all the cylinders 111, 112, 121, 122, 131 and 132 have the same dimensions, in particular the cylinders 111 and 112 of the same group 110.

In addition, the device 101 differs from the device 1, since it has only one proportional distributor 171 connected to the cylinders of the three groups 110, 120 and 130, instead of the three proportional distributors 71, 72 and 73 independent. The proportional distributor 171 controls the flows of operating fluid in and out of the cylinders 111, 112, 121, 122, 131 and 132, similarly to the proportional distributors 71, 72 and 73. The device 101 differs from the device 1 because it has flow divisors 110.1, 120.1 and 130.1 instead of conduits 10.1, 20.1 and 30.1. Each flow divider 110.1, 120.1 or 130.1 fulfills the function of synchronizing hydraulic unit of the cylinders belonging to the corresponding group 110, 120 or 130. The flow dividers 110.1, 120.1 and 130.1 are therefore connected to the cylinders

111, 112, 121, 122, 131 and 132 so as to form three separate groups 110, 120 and 130 of cylinders. Each group 110, 120 or 130 includes two cylinders 111-112, 121-122 or 131-132 which are connected by a flow divider 110.1, 120.1 or 130.1. Two cylinders, such as 111-121 or 112-122 belonging to two distinct groups 110, 120 are not connected by a flow divider 110.1, 120.1 or 130.1.

The description of the structure and operation of the flow divider 110.1 is detailed below in connection with FIG. 8. Insofar as the flow dividers 102.1 and 130.1 are identical or similar to the flow divider 110.1, the description of the divider flow rate 110.1 can be transposed to flow divisors 102.1 and 130.1.

The flow divider 110.1 comprises two hydraulic motors 110.2 and 110.3, as well as a common shaft 110.4. The hydraulic motor 110.2 is connected to the first chamber 111.1 of the cylinder 111. The hydraulic motor 110.3 is connected to the first chamber 112.1 of the cylinder 112. The common shaft 1 10.4 mechanically links the hydraulic motors 1 10.2 and 1 10.3 to each other, so that the hydraulic motors 1 10.2 and 1 10.3 have the same speed of rotation around the common shaft 1 10.4. Thus, the flow of operating fluid in the hydraulic motor 1 10.2 is equal to the flow of operating fluid in the hydraulic motor 1 1 0.3. Thus the flow of operating fluid flowing to or from the first chamber 1 1 1 .1 is equal to the flow of operating fluid flowing to or from the first chamber 1 12.1. Therefore, the hydraulic synchronizing member formed by the flow divider 1 1 0.1 synchronizes the distances traveled by the pistons 1 1 1 .4 and 1 12.4 in the direction Y.

As an alternative to flow dividers, the hydraulic synchronization members may be formed by volume or quantity dividers, for example by linear dividers, each comprising a multi-chamber jack, one rod of which simultaneously actuates several pistons. According to a variant of the invention not shown, the control device of Figure 1 may comprise a single proportional distributor which is common to the separate groups, instead of three proportional distributors. Conversely, according to another variant not shown, instead of a common proportional distributor, the control device of Figure 8 may comprise three proportional distributors, one by group.

According to other variants of the invention not shown: the faces of the pistons may not be flat, but for example curved or left; the sheath valve may have a cylindrical ring shape with a non-circular base, for example based on the acrylic, a non-cylindrical annular shape, for example a prismatic square base; the rods are not directly attached to the slider valve, but are connected to it by means of respective mechanical connecting members such as nuts; the main direction of movement of the slider valve can be horizontal, or even oblique, rather than vertical; at least one group may include three or more jacks; in a variant where three jacks form a group, two ducts connect these three cylinders in series; the difference between the squares of the internal diameters of two consecutive cylinders is the square of the diameter of the rod of the jack having the largest diameter; two distinct groups may have different numbers of jacks; at least one hydraulic synchronizing member may be provided for connecting two cylinders to each other only in case of emergency, when the sleeve valve must be closed quickly; in normal operation, these two cylinders are not connected by this hydraulic device.

A device according to the present invention thus ensures a very precise synchronization between its cylinders thanks to their hydraulic synchronization and their mechanical synchronization. A device according to the present invention is easy to adjust and requires little maintenance. A hydraulic machine according to the invention is therefore reliable.

Claims

1. Device (1; 101) for controlling the movement of a sleeve valve (2; 102) of a hydraulic machine (M) having a blade wheel (R), the sleeve valve (2; 102) defining a closed contour and being movable between an open position and a closed position of at least one pipe (5) for supplying water to the impeller (R),

the device (1; 101) comprising at least four cylinders (11, 12, 21, 22, 31, 32, 111, 112, 121, 122, 131, 132) with double hydraulic action, each cylinder (11, 12, 21 , 22, 31, 32; 111, 112, 121, 122, 131, 132) comprising:

a rod (11.3, 12.3),

a piston (11.4, 12.4, 111.4, 112.4),

a first chamber (11.1, 12.1, 111.1, 112.1) and

a second chamber (11.2, 12.2, 111.2, 112.2),

the first chamber (11.1, 12.1; 111.1, 112.1) and the second chamber (11.2, 12.2; 111.2, 112.2) being adapted to receive an actuating fluid, the piston (11.4, 12.4, 111.4, 112.4) being connected to the rod (11.3, 12.3) so as to separate the first chamber (11.1, 12.1; 111.1, 112.1) from the second chamber (11.2, 12.2; 111.2, 112.2), the first chamber (11.1, 12.1; 111.1, 112.1) being located on the side of the rod (11.3, 12.3) relative to the piston (11.4, 12.4, 111.4, 112.4) and the second chamber (11.2, 12.2, 111.2, 112.2) being located on the side opposite the rod (11.3, 12.3) by relative to the piston (11.4, 12.4, 111.4, 112.4), the rods (11.3, 12.3) being adapted to be connected to the sleeve valve (2; 102) at locations (P11, P12, P21, P22, P31, P32 ) located on a perimeter (C2) adapted to coincide with the contour of the sleeve valve (2; 102),

the device (1; 101) being characterized in that it further comprises at least two hydraulic timing members (10.1, 20.1, 30.1, 110.1, 120.1, 130.1) the distances traveled by pistons (11.4, 12.4, 111.4, 112.4) in the main direction (Y) of movement of the sleeve valve (2; 102), the synchronizing hydraulic members (10.1, 20.1, 30.1, 110.1, 120.1, 130.1) being connected to the cylinders (11, 12, 21). , 22, 31, 32, 111, 112, 121, 122, 131, 132) so as to form at least two groups (10, 20, 30; 110, 120, 130) separate from cylinders, each group (10, 20, , 110, 120, 130) encompassing at minus two cylinders (11-12, 21-22, 31-32, 111-112, 121-122, 131-132) connected by at least one synchronizing hydraulic unit (10.1, 20.1, 30.1, 110.1, 120.1, 130.1) two cylinders (11, 21, 31, 12, 22, 32, 111, 112, 121, 122, 131, 132) belonging to two distinct groups (10, 20, 30, 110, 120, 130) not being connected by a synchronizing hydraulic unit (10.1, 20.1, 30.1, 110.1, 120.1, 130.1).

2. Device (1; 101) according to claim 1, characterized in that the locations (P11, P12, P21, P22, P31, P32) are distributed on the perimeter (C2) so that the stiffness of the sheath valve (2) helps to synchronize the distances traveled by pistons (11.4, 21.4, 111.4, 112.4) belonging to distinct groups (10, 20, 30, 110, 120, 130), in the main direction (Y) of movement of the slider valve (2; 102).

3. Device (1) according to one of claims 1 or 2, characterized in that at least one hydraulic synchronizing member comprises a conduit (10.1, 20.1, 30.1) arranged to connect in series at least two cylinders (11- 12, 21-22, 31-32) belonging to the same group (10, 20, 30), namely a first jack and a second jack, said hydraulic synchronizing member (10.1, 20.1, 30.1) being adapted for the operating fluid flow from the first chamber (11.1) of a first cylinder (11, 21, 31) to the second chamber (12.2) of a second cylinder (12, 22, 32), the second cylinder (12 , 22, 32) being consecutive to the first ram (11, 21, 31) in their group (10, 20, 30), the area (S11.41) of the face (11.41) of the piston (11.4) delimiting the first chamber (11.1) of the first jack (11, 21, 31) being approximately equal to the area (S12.42) of the face (12.42) of the piston (12.4) delimiting the second chamber (12.2) of the second rin (12, 22, 32).

4. Device (1; 101) according to one of the preceding claims, characterized in that the number of cylinders (11, 12, 21, 22, 31, 32; 111, 112, 121, 122, 131, 132) is between 5 and 30.

5. Device (1; 101) according to one of the preceding claims, characterized in that the groups (10, 20, 30; 110, 120, 130) include the same number of cylinders (11, 12, 21, 22, 31, 32, 111, 112, 121, 122, 131, 132).

6. Device (1; 101) according to claims 4 and 5, characterized in that it comprises at least three groups (10, 20, 30; 110, 120, 130) of cylinders and in that each group (10, 20, 30, 110, 120, 130) includes two jacks (11-12, 21-22, 31-32, 111-112, 121-122, 131-132).

7. Device (1) according to one of the preceding claims, characterized in that two consecutive locations (P11, P21) on said perimeter (C2) correspond to cylinders (11, 21; 111, 121) belonging to two groups ( 10, 20, 30, 110, 120, 130).

8. Device (1; 101) according to claims 6 and 7, characterized in that the locations (P11, P12, P21, P22, P31, P32) are uniformly distributed over said perimeter (C2), in that said perimeter ( C2) is in the form of a circle and in that the locations (P11, P12, P21, P22, P31, P32) corresponding to the two cylinders (11, 12, 21, 22, 31, 32, 111, 112, 121, 122 131, 132) of a group (10, 20, 30; 110, 120, 130) are diametrically opposed.

9. Device (1; 101) according to one of the preceding claims, characterized in that the first chamber (11.1, 12.1; 111.1, 112.1) and the second chamber (11.2, 12.2; 111.2, 112.2) of each cylinder (11 , 12, 21, 22, 31, 32, 111, 112, 121, 122, 131, 132) are generally in the form of cylinders with circular bases.

10. Device (1) according to claims 3 and 9, characterized in that, for a first cylinder (11) and a second cylinder (12) belonging to the same group (10, 20, 30), the difference between the square of the inner diameter (D11) of the first jack (11) and the square of the inner diameter (D12) of the second jack (12) is the square of the diameter (D11.3) of the rod (11.3) of the first jack (11).

11. Device (1; 101) according to one of the preceding claims, characterized in that it further comprises a control unit (4; 104) and discrete supply means and / or discrete evacuation (74). , 75, 76; 174, 175, 176) in actuating fluid for each cylinder (11, 12, 21, 22, 31, 32; 111, 112, 121, 122, 131, 132), in that each cylinder (11, 12, 21, 22, 31, 32, 111, 112, 121, 122, 131, 132) is equipped with at least one sensor (11.5, 12.5) adapted to emit signals representative of the position of the piston ( 11.4, 12.4, 111.4, 112.4) corresponding to the direction of actuation of the jack (Y), the control unit (4; 104) being arranged to collect said signals and adapted to drive the discrete supply means and / or Discrete discharge means (74, 75, 76; 174, 175, 176) taking into account the positional deviations, in the main direction (Y) of movement of the sleeve valve (2; 102), between cylinders (11 , 12, 21, 22, 31, 32; 111, 112, 121, 122, 131, 132) belonging to the same group (10, 20, 30; 110, 120, 130).

12. Device (1; 110) according to claim 11, characterized in that it further comprises means of continuous supply and / or continuous discharge (71, 72, 73; 171) of fluid actuating cylinders (11, 12, 21, 22, 31, 32, 111, 112, 121, 122, 131, 132) and in that the control unit (4; 104) is adapted to drive the continuous supply means and / or continuous discharge (71, 72, 73; 171) taking into account the positional differences between cylinders (11, 12, 21, 22, 31, 32; 111, 112, 121, 122, 131, 132 ) belonging to distinct groups (10, 20, 30; 110, 120, 130).

13. Hydraulic machine (M), of the turbine, pump or turbine-pump type, comprising a bladed wheel (R) and a sleeve valve (2; 102) movable between an open position and a closed shutter position. at least one pipe (5) for supplying water to the impeller (R), the hydraulic machine (M) being characterized in that it further comprises a device (1; 101) according to one of the preceding claims.